Hydraulic device



Sept 26, 1961 w. M. OSBORN 3,001,482

HYDRAULIC DEVICE Filed Jan. 24, 1958 2 Sheets-Sheet 1 INVENTOR.

F?- 5. ZbW/m M 055012Z ATTORNEYS Sept. 26, 1961 w. M. osBoRN HYDRAULIC DEVICE Filed Jan. 24, v1958 2 Sheets-Sheet 2 HTTRWEY5 United States Patent O 3,001,482 HYDRAULIC DEVICE William M. Osborn, 3349 Zuni St., Denver 11, Colo. Filed Jan. 24, 1958, Ser. No. 710,959 Claims. (Cl. 10S- 136) This invention relates to an improved hydraulic device, and particularly to an improved positive displacement pump of sturdy and simple construction for delivering one or several fluids in high volume and at'relatively high pressure While operating at a relatively low speed. The device may also be utilized as a fluid motor and as a combined fluid motor and pump.

An object of the invention is to provide a device of the type described, which is dynamically and hydrostatically Ibalanced so that it will operate smoothly and efciently with a minimum amount of wear on the moving parts.

Another object of the invention is to provide a device of the type described in which close operating tolerances between the moving parts maybe maintained.

Another object of the invention is to provide a positive displacement pump which can pump two uids at the same time and `at the same or at different pressures.

Another object of the invention is to provide a positive displacement pump which can be used to pump a iiuid having an extremely high or low temperature while the operating parts of the pump may be maintained within a less extreme temperature range.

Another object of the invention is to provide an improved radial-vaned rotary pump which can be operated with equal efficiency in either direction..

Another object of the invention is to provide an improved radial-vaned rotary pump which can be operated as a two-stage pump for a single liquid, asa pump for two diierent liquids, or as a combined pump and motor.

Still further object of the invention is to provide irnproved means for facilitating the opening and closing of the rotor vanes of an hydraulic device having rotor vanes which are radially movable.

These and other objects and advantages of the invention will be apparent from the following description taken in conjunction with the drawings in which FIG. 1 is a front elevational view of the hydraulic device of the present invention;

FIG. 2 is a side view of the device shown in FIG. 1;

FIG. 3 is a sectional view of the hydraulic device of FIGS. 1 and 2, taken on the line 3-3 of FIG. 2, and showing in detail the construction and arrangement of the rotor unit and an associated housing section;

FIG. 4 is a sectional view taken on the line 4 4 of FIG. 3 and further showing the manner of mounting the rotor unit with respect to its associated housing elements;

FIG. 5 is a perspective view of the rotor unit with the vanes removed;

FIG. 6 is a perspective view of one of the rotor vanes adapted to be mounted within one of the recesses of the rotor shown in FIG. 5;

FIG. 7 is a fragmentary view of a modified form of an adjustable abutment which can be used in the device illustrated in the preceding figures; and

FIG. 8 is an elevational view, partially diagrammatic, showing one of the ways in which the hydraulic device of the preceding gures may be used.

Referring now to the drawings in detail, and particularly to FIGS. 1, 2 and 3 thereof, the hydraulic device of the present invention is shown to comprise a pair of platelike end housing sections 12 and 14 having disposed therebetween an annular 0r ring-like intermediate housing section 16. The intermediate housing section v16 is formed integrally with a base 18 whereupon the device may be mounted upon a suitable support 20 by means of bolts 22. The housing sections 12, 14 and 16 are secured together in tightly assembled relationship by a plurality of bolts 24, which pass through suitable registering openings in the respective housing sections, and nuts 26 threadedly engaging the ends thereof.

The end housing sections 12 and 14 are provided with central openings 28 in which a shaft 30 is journaled. It will be understood that the end housing sections 12 and 14 may be provided with outwardly extending hubs and with suitable bearings (not shown), if so desired. However, it has been found that in small devices machined for close operating tolerances, such means are not necessary. The openings 28 through the end plates 12 and 14 are of a very slightly greater diameter than the diameter of the shaft 30, so as to provide close operating clearance only, thereby with certain other close-fitting parts described hereinafter preventing leakage of uid from the device and rendering the provision of separate seal means unnecessary.

Referring now particularly to FIGS. 3 and 4, it will be seen that the housing sections 12, 14 and 16 form a rotor chamber housing a cylindrical rotor 32. The width of the rotor 32 is substantially the same as the width of therannular housing section 16 between the end sections 12 and 14, sothat the side faces 34 of the rotor 32 confront the inner faces 36 of the end `housing sections 12 and 14 `with only very `close operating tolerance therebetween. The closely fitting rotor contributes to the effective sealing of the device against liquid leakage around the shaft 30.

The rotor chamber has an inner periphery 38 formed within the annular housing section 16, which is concentric with the periphery 40 of the rotor 32 and is suliciently spaced therefrom to provide working chambers 42 and 44 for radially movable vanes 46, 46a, 46h, 46c, 46a' and 46e carried by said rotor 32. Portions of the inner periphery 38 of the annular housing section 16 are removed to form a pair of diametrically opposed, relieved peripheral portions 48 and 50. The relieved portions 48 and 50 may extend the full width of the annular housing section 16 and may be concentric with the periphery 40 of the rotor 32. Shoulders 51, 51a, 51h and 51a define the beginning and ending of the relieved portions. 'I'he function of the relieved portions ,48 and 50 is to facilitate retraction of the rotor vanes 46, 46a1, etc., at the discharge end of a working chamber, as will hereinafter be more fully described.

The outer periphery of the annular housing section 16 is provided with a pair of oppositely disposed, enlarged portions or bosses 52 and 54, which are substantially in registry with the internal relieved peripheral portions 48 and 50.-

In accordance with a special feature of the present invention, the internal peripheral portions of the housing section 16 intermediate the relieved areas 4S and 50 (FIG. 3) are provided with radially movable, adjustable abutments 56 and 58 mounted within recesses 60 and 62 formed in the enlarged portions 52 and 54. The recesses 60 and 62 and abutments 56 and 58 extend for the full Width of the housing section 16 and the abutments 56 and 58 define the ends of the Working chambers 42 and 44. The abutments 56 and 58 are provided with inner ends 64 and 66, which have an arcuate configuration corresponding to the cylindrical periphery 40 of the rotor 32, so that they may closely engage the rotor periphery 40, as shown.

The abutments 56 and S8 are radially `movable within their recesses 60 and 62 and means are provided to control the degree of adjustment toward the rotor periphery 40. Such means, as shown in FIG. 3, comprise adjusting bolts 68 and 70, which threadedly engage bores 72 and 74 in the housing section 16. The bolts 68 and 70 56 and 58 may be urged into contact with the rotor periphery 40; and may then be locked into such position. It will be understood that the degree of pressure with which the abutments contact the rotor periphery is ad-V justed so that there is no substantial interference with the free rotation of the rotor 32. Readjustments may be made from time tol time to Vcompensate for any wear on the relatively ,movable parts.V

In a modified form of the invention, as shown in FIG. 7, a radially movable abutment 84 may =be -disposed in a recess 86 in the annular housing section 16 and may be resiliently urged toward the rotor periphery 40 by means of a spring y83 held within a bore 90 in the housing section 16 by means of a threaded plug 92. The structure of the oppositely disposed abutment is, of course, identical to the single illustrated form. By such means, Ithe abutments are constantly urged into engagement with the rotor periphery V40 to thereby insure a positive seal, preventing leakage of fluid between abutment and rotor.

Referring now to the rotor 32 it will be seen, particularly from FIG. 5, that this rotor is provided with a pluralityvof radial slots or recesses 94, Which extend for the entire width of the rotor body. The recesses 94 are provided in oppositely disposed pairs so as to insure dynamic balance of the rotor 32 for smooth rotor operation. Each recess 94 is provided with a rotor vane 46, or 46a, `46b, etc. (FIG. 3), which is of the same width as the rotor 32, so that the side faces 96 of the'rotor vanes are flush with the side faces 34 of the rotor- 32. r[he peripheral ends 98 of the rotor vanes 46, 46a, 46b, etc., are provided with substantially the same arcuate configuration as the inner periphery 38 of the housing section 16 which they contact when Ifully extended, for example, when in the position ofthe rotor vanes 46 and 46c, FIG. 3. The bottom ends 99 of rotor vanes 46, 46a, 46b, etc., are substantially spaced from the bottom 100 of the rotor recesses 94, even when such vanes are retracted to a position such that the peripheral ends 98 are iiush with the rotor periphery 40. The purpose of this spacing. is to facilitate the outward movement of the vanes, as will be later described in detail.

The lower portion of each rotor vane 46, 46a, 46h, etc., is provided with a borev101 to accommodate a shaft 102 (FIG. 4). The ends of the shaft 102 are provided with rotatable cam followers 104, which may be mounted by means of roller bearings 106 for smoother operation.

'I'he inner face 36- of each of the end housing sections 12 and 14 is provided with a cam track 108 which, as particularly shown in FIG. 3, communicates with lower portions of the rotor recesses 94- and receives cam followers 104 of lthe rotor vanes 46, 46a, 46h, etc. The configuration of the cam tracks 10S isl such that the rotor vanes 46 are permitted to be extended radially outwardly, fully into contact with the inner periphery 38 of housing section 16 during angular movements of` the rotor throughout the arcuate length `defined by the periphery 38. The cam track 108 changes in its path, asY

at 110, 111, 1112, and 113, `so that (assuming the rotor is turning counterclockwise as shown in FIG. 3) as rotor vanes 46, 46a, 46b, etc., reach shoulder 51 defining the beginning of relieved section 48, or 5'1b defining the beginning of a relieved section 50, the vanes are per.

mitted to retract', becoming fully retracted when they pass the abutments 56 or 5S, as the case mayy be, and are then. permitted tov become fully extended as they reach shoulders 51a and 51e.

The enlarged sections 52- and 54 of the housing` secv 4 tion 16 are provided with openings 114-115 and 116- 117 disposed on each side of the abutments 56 and 58, respectively, so as to provide for the liow of iiuid through the working cham-bers 42 and 44 of the device. These openings l114-115 and 116--117 are threaded at their ends and are provided with conventional pipe fittings 118. When the rotor 32 is turning in. a counterclockwise direction as viewed in FIG. 3, opening 116 consti tutes the inlet opening forv tiow of fluid into working chamber 42 and opening 114 constitutes the discharge opening for this fluid. Likewise, opening 115 constitutes the inlet opening for fiow of ui-d into the second working chamber 44 and opening -117 constitutes the discharge opening for this working chamber. Where the rotor 32 is to be run in the reverse or clockwise direction as viewed Vin FIG. 3, theinlet and discharge openings to the respective working chambers 42 and 44 are, of course, reversed-openings 1114 and 117 becoming inlet openings and openings 116 and 115'becoming discharge openings. ASince all parts are exactly symmetrical, it makes no difference as to the direction in which the rotor is turned.

In operation of the device as a pump, assuming coun- -terclockwise rotation of the rotor 32 (FIG. 3), fluid enters inlet opening 116, is picked up by a rising, vane such as a vane in the position of that designated as 46e., is carried around the working chamber 42 by suchrvane which becomes fully extended to the position shown by the vane indicated by the numeral 46, and' is then forced out of the discharge opening 114. At the same time, iiuid entering through the opening 115 is being picked up by the vanes as they travel through working chamber 44 and is discharged through the opening 117. The vanes 46, 46a, 4617, etc., once fully extended so that their ends 98 contact the inner housing periphery 38, as in the position of the vanes indicated by the numerals 46 and 46c shown in FIG. 3, do not retract until they pass shoulders 51 and 51h approaching the discharge openings. Centrifugal force facilitates the holding of the vanes in this outward position and the cam means, comprisingl the cam track 108 and cam followers 104 prevent retraction should this force be insufiicient. Fluid at discharge pressure 'then reacts downwardly upon the ends 98 of the vanes as they clear shoulders 51 and 51b and cause them to retract. The curvature of the cam 'tracks at, for example, and 112 prevents retraction of the vanes with a shot-like action and the cam path then assures that the vanes remain retracted while they pass abutments 56 and 58. The vanes are then extended as they clear the abutments -and approach shouldersl 51a and 51e by a combination of centrifugal force Vacting against the relatively low intake pressure and Vthe camming action of the cam followers 104 and cam track at 111and113.

The cam track 108 performsV a further important func# tion in facilitating the movement ofA the vanes duringy rotation of the rotor. Thus, as previously mentioned, the cam track interconnects the bottom portion of the recesses 94 in the rotor 32 and permits the passage of Huid' therebetween. Accordingly, as one vane,k for example vane 46a, retracts within its recess, fluid in the bottom portion of such recess is displaced through the cam track 108' into the bottom of a recess beneath a rising vane, as for example 4`6b, and helps to push this vane to its outward position. Accordingly, the vanes are operated to a large extent in their retractionV and opening by fluid pressure and centrifugal force, the cam path- 108 and cam followers 104 serving as an additional control factor to insure that the vanes are in proper position at all times. It will be seen that oppositely disposed vanes. are always in the same relative position, thereby. maintaining thev rotor in perfecty dynamic balance. It

will be noted, with` reference to FIG. 3, that the spacing of the vanes 46, 46a, 46b, 46c, 46d and 46e, andv the configuration of the camv tracks 108, are so related that the total volume of the clearances beneath all of the vanes remains constant, that is, as one or more vanes move inwardly, -another vane or vanes move outwardly at a rate to maintain a constant volume of the total of the clearances. It will also be notedthat the vanes have a length which is shorter than the length of the recesses, so that, whenthey arefully retracted, a clearance remains beneath the vanes, and that these clearances are always in communication with the cam tracks. 'Ihe clearances and the cam tracks, therefore, constitute a closed system which remains constant in `volume. Since no sealing means are provided between the rotor and the side walls 12 and 14, there will be a islightleakage from the high pressure side toward the cam tracks and the clearances beneath the'varies, and a "slight leakage fromf the cam tracks andthe clearances beneath the vanes toward the low pressure side. The clearances and the cam tracks will therefore he illed with uid at a pressure intermediate the high pressure side and the low pressure side, which pressure will act radially outwardly on the bottom of the vanes. As the volume constituting the clearances and cam tracks will remain constant, as explained above, the pressure will also remain substantially constant. By virtue of this arrangement, the end thrusts on the vanes are approximately one-half of what they would be if no fluid were trapped in the clearances and cam tracks, thereby reducing wear on the cam followers and cam tracks and requiring less work to operate the device as a pump, and offering less resistance when used as a motor. The clearances beneath the vanes provide passages for the iluid to pass from one side of the cam followers 104 to the other side.

In operating the device as a two-stage pump for a single fluid, the discharge opening 114 may be connected by means of suitable piping (not shown) to the intake opening 115. Fluid entering at 116 is then pumped through the one working chamber 42, out the discharge opening 114 into the inlet opening 115, through working chamber 44 and out of the discharge opening 117. In operating the device as ya pump for two different liquids, the inlets 116 and 115 are, of course, connected to different sources of uid.

Another manner of operating the `device as a pump is illustrated in FIG. 8. In accordance with this manner of operation, an extremely hot liquid which normally might overheat the pump parts and interfere with proper operation, enters through inlet pipe 120 and is pumped through chamber 44 of the pump, and out of outlet pipe 122. In order to prevent the rotor and other moving parts from overheating, the device is cooled by circulating a cooling liquid through the other working chamber 42 from inlet pipe 124, then out of a discharge pipe 126 through a heat exchange coil 123, where heat is given oi to a suitable cooling iluid entering through pipe 130 and out of pipe 132, and then back through the inlet pipe 124. The rotor is effectively cooled by running in direct contact with the cooling huid during one-half of each complete revolution. It will be understood, of course, that recirculation of cooling fluid through the heat exchanger can be omitted, if desired, where a suitable source of cooling iluid is constantly available. For example, it may be desired in some cases to pump `a hot liquid through one chamber while the pump is being cooled by another cooler liquid pumped through the other chamber for delivery to a specific usage. The double chamber pump of the invention is adaptable to a wide variety of such uses.

In the foregoing illustrations of operation of the device it has lbeen assumed that the rotor shaft 30 would be driven by a separate motor or other means (not shown), and that pump action would be eiected in both working chambers. However, in accordance with another arrangement, uid may be forced through one of the working chambers to drive the rotor, and the other cooling fluid under pressure might be utilized to both cool the rotor Vand impart rotary motion to such motor for pumpingV hot liquid through the other working chamber. It will also be understood that the device can be used as a fluid motor bysupplying fluid under pressure to both inlet openings. The rotor may be driven in either direction with equal facility. "The device may be used to pump uids at low pressures or, at pressures as high as 10,000 pounds per square inch, or greater. One relatively small unit has been found to deliver about 23 gallons of liquid per minute at 5000` p.s.i.g. when the shat is turned at 600 r.p.m. None of the parts works against conictng hydraulic pressures, and all revolving parts are in cornplete balance. The devicemay be fabricated to lit any installation, large or small. Thus, it is readily adaptable to units designed to deliver from less than one gallon per minute up to 5,000 gallons per minute, or greater.

It will be understood that various changes which will occur to those skilled in the art may be made without departing from the principles of fthe invention or the scope of the annexed claims.

I claim:

1. A hydraulic device, comprising: a housing having side walls and an annular member forming a rotor chamber; a shaft journaled in said side walls and extending through said rotor chamber; a rotor in said chamber fixed to said shaft, said rotor having a plurality of recesses extending radially inwardly around the periphery thereof for the full width of said rotor; vanes mounted in said recesses for radially inward and outward movement with respect to said rotor, said rotor chamber being concentric with the rotor and having a diameter greater than that of said rotor forming a working chamber surrounding the rotor to accommodate the radially outward movement of said vanes; means in a side wall forming a closed, liquidtilled channel separated from the working chamber connecting the lower portions of said recesses for iiuid pressure equalization below said vanes, said vanes having a radial length shorter than the radial length of the recesses so that, when in their retracted position with the outer ends of the vanes ush with the periphery of the rotor, the inner ends of the vanes provide a clearance permitting an uninterrupted connection between the respective recesses and the channel at all times, the vanes being related with each other so that, as one or more vanes move outwardly, another or other vanes move inwardly to maintain the total volume of the recesses beneath the vanes constant; a pair of diametrically opposed, radially movable abutments mounted within said housing and extending inwardly from the periphery of said rotor chamber and adapted to contact the periphery of said rotor to thereby define the limits of a pair of working chambers for said rotor vanes; means for adjusting the radial position of said abutments with respect to' said rotor; and uid inlet and outlet means through said housing on each side of said abutments.

2. The hydraulic device of claim 1 wherein said means for adjusting the radial position of said abutments with respect to said rotor comprise resilient means urging said abutments into contact with said rotor periphery.

3. The hydraulic device of claim l wherein said channel means for connecting the lower portions of said rotor recesses comprise a cam track in the housing and wherein said rotor vanes are provided with cam followers cooperating with said carn track to thereby control inward and outward movement of said rotor vanes.

4. The hydraulic device of claim 1 wherein said housing has a portion of its inner periphery relieved adjacent the discharge ends of the Working chambers, whereby iuid at discharge pressure may act upon the outer end of the rotor vanes as they approach the abutments to thereby cause said vanes to retract within their recesses.

5. A hydraulic device, comprising: a housing having side walls and an annular member forming a rotor chamber; a shaft journaled in said side walls and extending working chamber may be utilized as a pump. Thus, through said rotor chamber; arotor insaid chamber fixed t'o said shaft, said rotor chamber having a diameter greater than'that of said rotor to form a uid chamber surrounding said rotor; a pair of spaced abutments carried by said housing and extending across said fluid chamber todivide said chamber into two separated sections; movable vanes, carried by said rotor, and extendinginto said fluid chamber to form, in cooperation with said abutments, expansible and contractible working chambers; uid inlet and outlet means for each section on'each side of said abutments; the inlet means to one of said sections connected to a source of uid at a very high or veryl'ow temperature; means to connect the inlet and outletmeans of the other section in a closed circuit independent of said. one of said sections; and a heat exchange means in said closed circuit.

References Cited in the file of this, patent UNITED STATES PATENTS Adancourt Sept. 22, 1863, Stott Aug, 11, 1&74 Forsythe Feb. Z, 1886 Van Beresteyn June 28, `1904 Piatt ...f Oct. 11,l 1921 Bidwell Aug. 8, 1922. Piatt Feb. 6, 1923 Wingquist May 19, 1,925vv Scognamillo June 22, 1948.

FOREIGN PATENTS Sweden Mar. 3, 1925 Germany Sept. 20, 1905 

